WO2021148327A1 - Ensemble engrenage à vis sans fin pour système de direction assistée électromécanique, système de direction assistée, et véhicule - Google Patents

Ensemble engrenage à vis sans fin pour système de direction assistée électromécanique, système de direction assistée, et véhicule Download PDF

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Publication number
WO2021148327A1
WO2021148327A1 PCT/EP2021/050827 EP2021050827W WO2021148327A1 WO 2021148327 A1 WO2021148327 A1 WO 2021148327A1 EP 2021050827 W EP2021050827 W EP 2021050827W WO 2021148327 A1 WO2021148327 A1 WO 2021148327A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
rotor shaft
shaft
worm gear
housing
Prior art date
Application number
PCT/EP2021/050827
Other languages
German (de)
English (en)
Inventor
Tobias Sachs
Stefan Wilske
Mirko TRAUE
Original Assignee
Volkswagen Aktiengesellschaft
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Volkswagen Aktiengesellschaft filed Critical Volkswagen Aktiengesellschaft
Publication of WO2021148327A1 publication Critical patent/WO2021148327A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B62D5/0409—Electric motor acting on the steering column
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B62D5/0421—Electric motor acting on or near steering gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/081—Structural association with bearings specially adapted for worm gear drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/20—Land vehicles
    • F16C2326/24—Steering systems, e.g. steering rods or columns
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H2057/0213—Support of worm gear shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or bearings
    • F16H2057/0221—Axial adjustment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/126—Self-adjusting during operation, e.g. by a spring
    • F16H2057/127—Self-adjusting during operation, e.g. by a spring using springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/22—Toothed members; Worms for transmissions with crossing shafts, especially worms, worm-gears
    • F16H55/24—Special devices for taking up backlash

Definitions

  • the present invention relates to a worm gear arrangement for an electromechanical power steering system of a vehicle, an electromechanical power steering system with an electric motor and a vehicle with an electromechanical power steering system.
  • Steering systems in motor vehicles generally have electromechanical steering assistance that assists a driver in steering by means of a steering intervention.
  • steering systems of this type have, in particular, a steering drive which, when appropriately activated, introduces a steering assistance force and / or a steering assistance torque into the steering system and assists or automatically executes a steering movement.
  • a generic steering drive has an electric motor.
  • the quality of the steering assistance torque and / or the steering assistance force of an electric motor depends, among other things, on the correct positioning of the rotor in relation to the stator and, accordingly, on an air gap that is as uniform as possible between the rotor and the stator during operation of the electric motor.
  • An unfavorable mounting or an offset of the rotor to the stator lead to torque ripples and a noticeable feel.
  • a worm gear arrangement for an electromechanical power steering system of a vehicle has a rotor shaft for driving a rotor in an electric motor of the electromechanical power steering, a worm shaft non-rotatably connected to the rotor shaft, a housing in which the rotor shaft is at least partially arranged, and a bearing arrangement for the resilient mounting of the rotor shaft.
  • the bearing arrangement has a spring means which, with respect to a spring force direction of the spring means, is arranged parallel to the axial direction for a spring-loaded displacement of the rotor shaft in an axial direction of the rotor shaft.
  • Spring means can consequently be understood as a spring unit to compensate for play, in particular when deflecting with the power steering from one steering direction to another.
  • the position of the rotor in relation to the stator and / or the rotor position sensors of the rotor shaft are not or only insignificantly influenced here.
  • the wobbling of the drive shaft which includes the rotor shaft and the worm shaft, can be prevented or at least inhibited before this has any effect on the electric motor and / or the rotor position sensors.
  • the bearing arrangement according to the invention including the spring means can therefore be understood as a floating bearing arrangement for the rotor shaft to avoid and / or inhibit the wobbling of the drive shaft caused by the worm shaft or the worm gear.
  • the worm gear arrangement can have a worm gear which has the worm shaft and a worm wheel which is in engagement with the worm shaft.
  • the fact that the drive shaft is at least partially located in the housing can be understood to mean that the drive shaft extends at least partially through the housing.
  • the drive shaft is preferably arranged completely in the housing.
  • the housing can be understood as the motor housing of the electric motor, in which, however, not only the stator and the rotor, but also the worm gear are arranged. That is, the housing can be designed as a motor housing for receiving the rotor and an associated stator, the bearing arrangement being arranged within the housing.
  • the fact that the spring means is arranged parallel to the axial direction of the rotor shaft with respect to the spring force direction of the spring means can be understood to mean that the spring means is arranged parallel to the axial direction with respect to the main effective direction of the spring means.
  • the main direction of action can be understood to mean the direction in which the spring means can develop the strongest spring action.
  • the axial direction of the rotor shaft can be understood to mean a direction in which a central axis of the rotor shaft extends.
  • the parallelism between the direction of the spring force of the spring means and the axial direction can depend on a current deflection of the spring means and on any slight wobbling movement of the drive shaft. Accordingly, the parallel arrangement does not necessarily have to be understood as a perfectly parallel arrangement. Rather, the arrangement of the spring means parallel to the axial direction of the rotor shaft can be understood to mean a substantially parallel arrangement to the axial direction of the rotor shaft.
  • One side of the spring means can be attached to the housing and in particular to an inner wall of the housing.
  • the spring means is preferably attached directly or essentially directly to the housing or to the inner wall of the housing.
  • the bearing arrangement can thus be arranged in the housing in a particularly space-saving manner.
  • the spring means preferably has at least one helical spring and / or at least one plate spring.
  • the spring means can thus be made available in a cost-effective and structurally simple manner.
  • the spring means can furthermore have a plurality of spring elements which are each arranged with respect to a spring force direction of the respective spring element for a spring-loaded displacement of the rotor shaft in an axial direction of the rotor shaft, parallel to the axial direction. A particularly uniform application of spring force to the rotor shaft can thus be achieved.
  • the spring elements are preferably arranged next to one another in the circumferential direction of the rotor shaft.
  • the worm shaft is integrally connected to the rotor shaft, the electromechanical power steering being designed in a single pinion, dual pinion or C-EPS construction.
  • the spring means has a first spring element and a second spring element, with the first spring element being arranged in a first radial direction of the rotor shaft above the rotor shaft with a view to a cross section of the rotor shaft and the second spring element is arranged below the rotor shaft in a second radial direction of the rotor shaft, which extends opposite to the first radial direction.
  • the two spring elements are preferably arranged at a distance of approximately 180 ° from one another in the circumferential direction of the rotor shaft.
  • the spring means it is nevertheless possible for the spring means to have not only two, but also, for example, three, four or more spring elements.
  • the spring elements are preferably arranged at equal intervals from one another. With three spring elements, for example, by approx. 120 ° and with four spring elements, for example, by approx. 90 ° in the circumferential direction of the rotor shaft.
  • the spring means is an integral part of the housing. That is, parts of the housing can take over the function of the spring means, in particular of spring elements of the spring means, as they are described here. The degree of complexity of the worm gear arrangement can thus be further reduced.
  • the bearing arrangement in the case of a worm gear arrangement according to the invention, it is also possible for the bearing arrangement to have a floating bearing with a bearing play for the resilient deflection of the floating bearing by the spring means in the axial direction.
  • the rotor shaft can be moved, in particular displaced, in the axial direction of the rotor shaft by means of the bearing arrangement not only over the spring travel of the spring arrangement, but also essentially free of forces over the bearing play.
  • a particularly fast and low-resistance movement compensation of the tumbling drive shaft or worm shaft can be realized.
  • the fact that the bearing play is designed for the resilient deflection of the floating bearing in the axial direction can be understood to mean that parts of the floating bearing are mounted so as to be displaceable relative to one another in the axial direction of the rotor shaft by the spring means.
  • the floating bearing can be designed in the form of a ball or roller bearing with two bearing shells and a roller bearing, which is arranged between the two bearing shells and in particular has several balls or rollers, the bearing play being formed between the roller bearing and the bearing shells in the axial direction or the direction of the spring force .
  • the floating bearing has a shaft bearing attached to the rotor shaft, a housing bearing attached to the housing and a roller bearing positioned between the shaft bearing and the housing bearing, the shaft bearing and the housing bearing in the axial direction Are arranged non-destructively displaceable to one another.
  • the spring means is preferably arranged between the housing bearing and the housing. That is to say, the spring means is fastened to the housing with one end of the spring means and is fastened to the housing bearing with another end of the spring means.
  • the spring means has several spring elements, for example in the form of several helical springs or plate springs, one end of the respective spring element can be attached to an associated and separate housing bearing and another end of the respective spring element can be attached to an associated section of the housing, in particular on an inner wall or inner wall surface be attached to the housing.
  • Non-destructive displaceability can be understood to mean displaceability beyond a bearing clearance due to manufacturing tolerances. So can the bearing play between roller bearing and housing bearing and / or shaft bearing in the axial direction, for example, be more than 1 m or more than 3 mm.
  • the shaft bearing can be connected in one piece to the rotor shaft. This leads to a space-saving and stable construction of the worm gear arrangement.
  • the fact that the shaft bearing is integrally connected to the rotor shaft can be understood to mean that the rotor shaft is configured in one piece and / or monolithically including the shaft bearing.
  • the shaft bearing can be designed as an integral part of the rotor shaft during the manufacture of the rotor shaft or the drive shaft, which can include the rotor shaft and the worm shaft.
  • the housing bearing is connected in one piece to the housing in a worm gear arrangement according to the invention.
  • This also leads to a correspondingly space-saving and stable construction of the worm gear arrangement.
  • the fact that the housing bearing is connected in one piece to the housing can be understood to mean that the housing is designed in one piece and / or monolithically including the housing bearing.
  • the housing bearing can be designed as an integral part of the housing during manufacture of the housing.
  • the one-piece design of the housing including the housing bearing makes it possible to reliably and easily prevent the housing bearing from being inadvertently detached from the housing and / or a corresponding movement of the housing bearing relative to the housing.
  • fastening means for fastening a separate housing bearing to the housing can be dispensed with. This not only leads to a reduced degree of complexity of the worm gear arrangement, but also to advantageous component logistics.
  • the housing bearing is preferably configured on an inner wall section of the housing.
  • the bearing arrangement is arranged in the axial direction between the rotor and the worm shaft.
  • the bearing arrangement thus includes both a motor bearing and the spring bearing previously positioned on the drive shaft or worm shaft end can replace.
  • the worm gear arrangement or the electromechanical power steering as already mentioned above, can be configured with only two shaft bearings instead of three. This creates a reduced degree of complexity and a reduced weight, which is particularly advantageous in mobile applications. In addition, this can save costs.
  • the rotor shaft has a taper in a transition region from the rotor shaft to the worm shaft.
  • the bearing arrangement is preferably positioned between the taper and the rotor.
  • an electromechanical power steering system for a vehicle with an electric motor and a worm gear arrangement.
  • the power steering system according to the invention thus brings the same advantages as have been described in detail with reference to the worm gear arrangement according to the invention.
  • the electromechanical power steering is preferably configured in a single pinion, dual pinion or C-EPS design.
  • the rotor shaft and the worm shaft are preferably part of a one-piece drive shaft or a drive shaft made from one casting.
  • a vehicle with an electromechanical power steering system as described above is provided.
  • the vehicle thus also has the advantages described above.
  • the vehicle can be understood to mean, in particular, a road vehicle such as a car, a utility vehicle and a robot.
  • FIG. 1 shows an electromechanical power steering system with a worm gear arrangement according to a preferred embodiment of the present invention
  • FIG. 2 shows an enlarged detailed illustration of the power steering system shown in FIG. 1, and
  • FIG. 3 shows a vehicle with a power steering system according to the invention.
  • the power steering system 11 has an electric motor 16 and a worm gear arrangement 10.
  • the worm gear arrangement 10 has a rotor 14 for driving a rotor shaft 13 in an electric motor 16 of the electromechanical power steering system 11.
  • the electric motor 16 also has a stator 15, the rotor 14 being non-rotatably connected to the rotor shaft 13.
  • the rotor 14 and rotor shaft 13 are rotatably mounted in the stator 15.
  • the worm gear arrangement further comprises a worm shaft 17 connected in a rotationally fixed manner to the rotor shaft 13. More precisely, the rotor shaft 13 and the worm shaft 17 are designed as part of a one-piece drive shaft 28.
  • the power steering 11 is designed according to the single pinion design.
  • the worm gear arrangement 10 also has a housing 18 in which the drive shaft 28 including the rotor shaft 13 and the worm shaft 17 is arranged. Furthermore, the housing comprises the rotor 14 and the stator 15 of the electric motor 16. In addition, the worm gear arrangement 10 has a bearing arrangement 19 for the resilient mounting of the rotor shaft 13.
  • the bearing arrangement 19 comprises a spring means 20 which, with respect to a spring force direction F1 of the spring means 20, is arranged for a spring-loaded displacement of the rotor shaft 13 in an axial direction D1 of the rotor shaft 13, parallel to the axial direction D1.
  • the spring means 20 has a first spring element 21 and a second spring element 22, with the first spring element 21 in a first radial direction R1 of the rotor shaft 13 above the rotor shaft 13 looking at a cross section of the rotor shaft 13 is arranged and the second spring element 22 is arranged in a second radial direction R2 of the rotor shaft 13, which extends opposite to the first radial direction R1, under the rotor shaft 13.
  • the illustrated bearing arrangement 19 is arranged between the rotor 14 and the worm shaft 17 in the axial direction D1.
  • FIG. 2 shows an enlarged detailed illustration of the worm gear arrangement 10 shown in FIG the rotor shaft 13 has.
  • the floating bearing 23 has a shaft bearing 24 fastened to the rotor shaft 13, a housing bearing 25 fastened to the housing 18 and a roller bearing 26 positioned between the shaft bearing 24 and the housing bearing 25.
  • the shaft bearing 24 and the housing bearing 25 are each designed in cross section in the form of a bearing shell.
  • the roller bearing 26 has a plurality of cylindrical rollers.
  • the shaft bearing 24, the housing bearing 25 and the roller bearing 26 are accordingly designed in the form of a roller bearing. Due to the bearing play in the roller bearing, the shaft bearing 24 and the housing bearing 25 are arranged to be displaceable to one another in the axial direction D1 or the spring force direction F1, respectively, without being destroyed.
  • a vehicle 12 is shown in the form of a car with an electromechanical power steering system 11 as described above, which is arranged in the front part of the vehicle near the wheels.
  • the invention permits further design principles.
  • the invention should not be viewed as restricted to the exemplary embodiments explained with reference to the figures. It is thus possible for the shaft bearing 24 to be connected in one piece to the rotor shaft 13.
  • the housing bearing 25 can also be connected in one piece to the housing 18.
  • a corresponding ball bearing could also be used in the bearing arrangement 19.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Gear Transmission (AREA)
  • Power Steering Mechanism (AREA)

Abstract

La présente invention concerne un ensemble engrenage à vis sans fin (10) pour un système de direction assistée électromécanique (11) d'un véhicule (12), comprenant : un arbre de rotor (13) pour entraîner un rotor (14) dans un moteur électrique (16) du système de direction assistée électromécanique (11) ; un engrenage à vis sans fin (17) raccordé à l'arbre de rotor (13) pour une rotation conjointe ; un logement (18) dans lequel l'arbre de rotor (13) est au moins partiellement disposé ; et un ensemble palier (19) pour supporter de manière élastique l'arbre de rotor (13), l'ensemble palier (19) comportant un moyen de ressort (20), qui, par rapport à une direction de force de ressort (F1) du moyen de ressort (20), est disposé parallèlement à une direction axiale (D1) de l'arbre de rotor (13) pour un déplacement à ressort de l'arbre de rotor (13) dans la direction axiale (D1). La présente invention porte également sur un système de direction assistée électromécanique (11) présentant un ensemble engrenage à vis sans fin (10) selon l'invention et sur un véhicule (12) présentant un système de direction assistée (11) selon l'invention.
PCT/EP2021/050827 2020-01-20 2021-01-15 Ensemble engrenage à vis sans fin pour système de direction assistée électromécanique, système de direction assistée, et véhicule WO2021148327A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020200578.8 2020-01-20
DE102020200578.8A DE102020200578A1 (de) 2020-01-20 2020-01-20 Schneckengetriebeanordnung für eine elektromechanische Hilfskraftlenkung, Hilfskraftlenkung und Fahrzeug

Publications (1)

Publication Number Publication Date
WO2021148327A1 true WO2021148327A1 (fr) 2021-07-29

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ID=74191746

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2021/050827 WO2021148327A1 (fr) 2020-01-20 2021-01-15 Ensemble engrenage à vis sans fin pour système de direction assistée électromécanique, système de direction assistée, et véhicule

Country Status (2)

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DE (1) DE102020200578A1 (fr)
WO (1) WO2021148327A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0943842A1 (fr) * 1998-03-19 1999-09-22 Mannesmann VDO Aktiengesellschaft Engrenage à vis sans fin
DE10217123A1 (de) 2002-04-17 2003-12-18 Bosch Gmbh Robert Spielfreies Lenkgetriebe
DE102006015571A1 (de) * 2006-04-04 2007-10-11 Daimlerchrysler Ag Elektromaschine mit Wälzlagerung

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9812844D0 (en) 1998-06-16 1998-08-12 Lucas Ind Plc Improvements relating to electrical power assisted steering
DE102010029266A1 (de) 2010-05-25 2011-12-01 Zf Lenksysteme Gmbh Kugelumlaufgetriebe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0943842A1 (fr) * 1998-03-19 1999-09-22 Mannesmann VDO Aktiengesellschaft Engrenage à vis sans fin
DE10217123A1 (de) 2002-04-17 2003-12-18 Bosch Gmbh Robert Spielfreies Lenkgetriebe
DE102006015571A1 (de) * 2006-04-04 2007-10-11 Daimlerchrysler Ag Elektromaschine mit Wälzlagerung

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